EP2345823A1 - Universelles gleichlauffestgelenk, verfahren zur herstellung eines universellen gleichlauffestgelenks sowie lagervorrichtung mit dem universellen gleichlauffestgelenk zur verwendung in einem antriebsrad - Google Patents

Universelles gleichlauffestgelenk, verfahren zur herstellung eines universellen gleichlauffestgelenks sowie lagervorrichtung mit dem universellen gleichlauffestgelenk zur verwendung in einem antriebsrad Download PDF

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Publication number
EP2345823A1
EP2345823A1 EP09824685A EP09824685A EP2345823A1 EP 2345823 A1 EP2345823 A1 EP 2345823A1 EP 09824685 A EP09824685 A EP 09824685A EP 09824685 A EP09824685 A EP 09824685A EP 2345823 A1 EP2345823 A1 EP 2345823A1
Authority
EP
European Patent Office
Prior art keywords
joint member
track grooves
constant velocity
velocity universal
track
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP09824685A
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English (en)
French (fr)
Other versions
EP2345823A4 (de
EP2345823B1 (de
Inventor
Masazumi Kobayashi
Kisao Yamazaki
Minoru Ishijima
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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Filing date
Publication date
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of EP2345823A1 publication Critical patent/EP2345823A1/de
Publication of EP2345823A4 publication Critical patent/EP2345823A4/de
Application granted granted Critical
Publication of EP2345823B1 publication Critical patent/EP2345823B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/076—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0015—Hubs for driven wheels
    • B60B27/0021—Hubs for driven wheels characterised by torque transmission means from drive axle
    • B60B27/0026—Hubs for driven wheels characterised by torque transmission means from drive axle of the radial type, e.g. splined key
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0015—Hubs for driven wheels
    • B60B27/0036—Hubs for driven wheels comprising homokinetic joints
    • B60B27/0042—Hubs for driven wheels comprising homokinetic joints characterised by the fixation of the homokinetic joint to the hub
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0094—Hubs one or more of the bearing races are formed by the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F16C35/0635—Fixing them on the shaft the bore of the inner ring being of special non-cylindrical shape which co-operates with a complementary shape on the shaft, e.g. teeth, polygonal sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22309—Details of grooves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2250/00—Manufacturing; Assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/10—Surface characteristics; Details related to material surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/12—Mounting or assembling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y10T29/49643—Rotary bearing
    • Y10T29/49679—Anti-friction bearing or component thereof
    • Y10T29/4968—Assembling of race, cage, and rolling anti-friction members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y10T29/49696—Mounting

Definitions

  • the present invention relates to a fixed type constant velocity universal joint, a method of manufacturing the fixed type constant velocity universal joint, and a driving-wheel bearing unit using the fixed type constant velocity universal joint, the fixed type constant velocity universal joint being used, for example, in a power transmission system for automobiles and various industrial machines, and allowing only angular displacement between two shafts on a driving side and a driven side.
  • the drive shaft described above includes a propeller shaft for transmitting a rotational driving force from a transmission to a differential and a half shaft for transmitting a rotational driving force from the differential to a wheel.
  • a Birfield type constant velocity universal joint BJ
  • DOJ double offset type constant velocity universal joint
  • the fixed type constant velocity universal joint of the BJ type includes, as main components, an outer joint member having an inner spherical surface provided with a plurality of track grooves extending in an axial direction, an inner joint member having an outer spherical surface provided with track grooves extending in the axial direction in pairs with the track grooves of the outer joint member, a plurality of balls interposed between the track grooves of the outer joint member and the track grooves of the inner joint member so as to transmit torque, and a cage interposed between the inner spherical surface of the outer joint member and the outer spherical surface of the inner joint member so as to hold the balls.
  • the plurality of balls are respectively housed in pockets formed in the cage and equiangularly arranged.
  • the outer joint member and the inner joint member in the fixed type constant velocity universal joint are generally manufactured by the following procedure.
  • a columnar billet is roughly formed into a shape of the outer joint member or the inner joint member by hot forging, warm forging, or cold forging, and then lathing is performed on an outer spherical surface, an inner spherical surface, and an end surface of this raw material.
  • heat treatment is performed, and then the outer spherical surface, the inner spherical surface, and the track grooves are finished by grinding, quenched-steel trimming, or the like. In this manner, the outer joint member and the inner joint member are manufactured.
  • the outer joint member and the inner joint member manufactured as described above are selectively combined with each other so that PCD gaps and the like fall within a range of defined values.
  • outer joint members 210 and inner joint members 220 are ranked according to a PCD, and cages 240 having pocket widths in conformity with balls 230 are ranked according to the pocket widths.
  • the outer joint members 210, the inner joint members 220, the balls 230, and the cages 240 ranked into a plurality of ranks as described above, in consideration of combinations of components including the outer joint members 210, the inner joint members 220, the balls 230, and the cages 240 so that the PCD gaps and the like fall within the range of the defined values, and based on a matching table, the outer joint members 210, the inner joint members 220, the balls 230, and the cages 240 are selected and combined with each other (for example, refer to Patent Literatures 1 and 2).
  • the outer joint members 210 and the inner joint members 220 which are described above as components of the conventional fixed type constant velocity universal joint are manufactured through forging, lathing, heat treatment, and finally, a finishing process such as grinding on the track grooves.
  • the finishing process performed in this manner on the track grooves after forging, lathing, and heat treatment has the following inconveniences: facilities and tools for the finishing process on the track grooves involve high cost; the finishing process takes a long time period; and yields of raw materials are poor.
  • an inner component including the inner joint member 220, the balls 230, and the cage 240 is incorporated into the outer joint member 210, from among the many ranked outer joint members 210, inner joint members 220, balls 230, and cages 240, the components including the outer joint members 210, the inner joint members 220, the balls 230, and the cages 240 are selected based on the matching table and combined with each other so that the PCD gaps and the like fall within the range of the defined values.
  • the selection and combination have a problem in that the combination of the components involves time and effort, which leads to poor workability.
  • the present invention has been proposed in view of the above-mentioned problems. It is an object of the present invention to provide at low cost a fixed type constant velocity universal joint, a method of manufacturing the fixed type constant velocity universal joint, and a driving-wheel bearing unit using the fixed type constant velocity universal joint, the fixed type constant velocity universal joint including an outer joint member or an inner joint member which is manufactured in a simplified manner.
  • the present invention provides a fixed type constant velocity universal joint including: an outer joint member having an inner spherical surface provided with a plurality of track grooves extending in an axial direction; an inner joint member having an outer spherical surface provided with a plurality of track grooves extending in the axial direction in pairs with the plurality of track grooves of the outer joint member; a plurality of balls interposed between the plurality of track grooves of the outer joint member and the plurality of track grooves of the inner joint member so as to transmit torque; and a cage interposed between the inner spherical surface of the outer joint member and the outer spherical surface of the inner joint member so as to hold the plurality of balls, at least one of the plurality of track grooves of the outer joint member and the plurality of track grooves of the inner joint member being formed by cold-forging finishing, in which components including the outer joint member, the inner joint member, the plurality of balls, and the cage are assembled to each
  • the present invention provides a method of manufacturing a fixed type constant velocity universal joint, the fixed type constant velocity universal joint including: an outer joint member having a cup-like shape so as to open at one end and an inner spherical surface provided with a plurality of track grooves extending in an axial direction; an inner joint member having an outer spherical surface provided with a plurality of track grooves extending in the axial direction in pairs with the plurality of track grooves of the outer joint member; a plurality of balls interposed between the plurality of track grooves of the outer joint member and the plurality of track grooves of the inner joint member so as to transmit torque; and a cage interposed between the inner spherical surface of the outer joint member and the outer spherical surface of the inner joint member so as to hold the plurality of balls, at least one of the plurality of track grooves of the outer joint member and the plurality of track grooves of the inner joint member being formed by cold-forging finishing, the method including: ranking, according to outer diameters of the outer
  • the PCD of the outer joint member represents a pitch circle diameter of each of the plurality of balls in a state of being held in contact with the plurality of track grooves of the outer joint member
  • the PCD of the inner joint member represents a pitch circle diameter of each of the plurality of balls in a state of being held in contact with the plurality of track grooves of the inner joint member
  • At least one of the plurality of track grooves of the outer joint member and the plurality of track grooves of the inner joint member are formed by cold-forging finishing.
  • the plurality of track grooves are formed only by cold-forging finishing.
  • many conventional machine processes performed after cold forging can be omitted such as a trimming process and a grinding process.
  • a yield increases, and hence cost of the constant velocity universal joint can be reduced.
  • the components including the outer joint member, the inner joint member, the plurality of balls, and the cage are combined with each other based on the simple matching in which the plurality of balls and the cage each having the rank corresponding to the measured value of the PCD of the arbitrarily selected outer joint member and to the measured value of the PCD of the arbitrarily selected inner joint member are selected with respect to the arbitrarily selected outer joint member and the arbitrarily selected inner joint member.
  • the components including the outer joint member, the inner joint member, the plurality of balls, and the cage are combined with each other by the following: ranking, according to the outer diameters of the plurality of balls, the cages having the pocket widths in conformity with the outer diameters of the plurality of balls; measuring the PCD of the arbitrarily selected outer joint member and the PCD of the arbitrarily selected inner joint member; and matching in which the plurality of balls and the cage each having the rank corresponding to the measured value of the PCD of the arbitrarily selected outer joint member and to the measured value of the PCD of the arbitrarily selected inner joint member are selected with respect to the arbitrarily selected outer joint member and the arbitrarily selected inner joint member.
  • each of the plurality of track grooves of the outer joint member and the plurality of track grooves of the inner joint member have a lateral-sectional Gothic arch shape of being held in angular contact with the plurality of balls, and that an angle formed by the angular contact be set to range from 35° to 45°.
  • cutout round portions be formed at least at parts corresponding to ball-contact points.
  • the cutout round portions are formedat least at the parts corresponding to the ball-contact points, the following advantage can be obtained: at the time of operation of the constant velocity universal joint at high angles, specifically, even when angles expected during use are exceeded for some reason so that each of the plurality of balls comes to a position at an axial end portion of each of the plurality of track grooves of the outer joint member or each of the plurality of track grooves of the inner joint member, the cutout round portions prevent each of the plurality of balls from biting into the axial end portion.
  • the plurality of track grooves and the cutout round portions of the outer joint member and the plurality of track grooves and the cutout round portions of the inner joint member be formed by simultaneous cold-forging finishing.
  • the plurality of track grooves and the cutout round portions of the outer joint member and the plurality of track grooves and the cutout round portions of the inner joint member are formed by simultaneous cold-forging finishing, it is unnecessary to perform, after formation of the plurality of track grooves, a machining process such as lathing and grinding finishing after heat treatment.
  • the plurality oftrack grooves and the cutout round portions are formed only by simultaneous cold-forging finishing, with the result that formation of the cutout round portions can be simplified, and cost of the constant velocity universal joint can be reduced.
  • the outer joint member include the following formed by cold-forging finishing: inlet chamfers formed along an entire opening periphery; track chamfers formed along boundary portions between the inner spherical surface and the plurality of track grooves; and track-inlet chamfers formed along boundary portions between the plurality of track grooves and the inlet chamfers, and that parts except for a boot recessed groove formed in an outer peripheral surface of the opening end of the outer joint member be formed by cold-forging finishing.
  • the inlet chamfers, the track chamfers, and the track-inlet chamfers of the outer joint member are formed by cold-forging finishing
  • the inlet chamfers, the track chamfers, and the track-inlet chamfers are formed only by cold-forging finishing.
  • many conventional machine processes performed af ter cold forging can be omitted such as a trimming process and a grinding process.
  • a yield further increases, and hence cost of the constant velocity universal joint can be further reduced.
  • the parts except for the boot recessed groove formed in the outer peripheral surface of the outer joint member are formed by cold-forging finishing, the outer peripheral surface can be endowed with higher hardness, and torsional strength can be increased.
  • work man-hours are reduced, and hence cost of the constant velocity universal joint can be reduced.
  • the plurality of track grooves and the track-inlet chamfers of the outer joint member be formed by simultaneous cold-forging finishing.
  • the plurality of track grooves and the track-inlet chamfers of the outer joint member are formed by simultaneous cold-forging finishing, it is unnecessary to perform, after formationof thepluralityof trackgrooves, amachiningprocess such as lathing and grinding finishing after heat treatment.
  • amachiningprocess such as lathing and grinding finishing after heat treatment.
  • the plurality of track grooves and the track-inlet chamfers are formed only by simultaneous cold-forging finishing, with the result that formation of the track-inlet chamfers can be simplified, and cost of the constant velocity universal joint can be reduced.
  • the track chamfers formed along the boundary portions between the inner spherical surface and the plurality of track grooves of the outer joint member and track chamfers formed along boundary portions between the outer spherical surface and the plurality of track grooves of the inner joint member be each formed in a round shape.
  • the round-shaped track chamfers may be formed not by cold-forging finishing but by a machining process such as lathing after cold forging and grinding finishing after heat treatment.
  • the plurality of track grooves and the track chamfers of the outer joint member and the plurality of track grooves and the track chamfers of the inner joint member be formed by simultaneous cold-forging finishing.
  • the plurality of track grooves and the track chamfers of the outer joint member and the plurality of track grooves and the track chamfers of the inner joint member are formed by simultaneous cold-forging finishing, it is unnecessary to perform, after formation of the plurality of track grooves, a machining process such as lathing and grinding finishing after heat treatment.
  • a machining process such as lathing and grinding finishing after heat treatment.
  • the plurality of track grooves and the track chamfers are formed only by simultaneous cold-forging finishing, with the result that formationof the track chamfers canbe simplified, and cost of the constant velocity universal joint can be reduced.
  • slit grooves extending in the axial direction be formed between the plurality of track grooves adjacent to each other in a circumferential direction along the inner spherical surface of the outer joint member, and that a width dimension of each of the slit grooves be set to range from 5% to 30% of a maximum width dimension of the inner spherical surface between the plurality of track grooves adjacent to each other in the circumferential direction.
  • the inner spherical surface can be formed with desired shape accuracy.
  • the width dimension of each of the slit grooves is set to range from 5% to 30%, it is easy to demold the outer joint member from the molding die at the time of cold-forging finishing.
  • an area required for the inner spherical surface of the outer joint member can be secured, and hence required strength and durability can be secured.
  • the width dimension of each of the slit grooves is smaller than 5%, it is difficult to demold the outer race joint member from the molding die at the time of cold-forging finishing. Meanwhile, when the width dimension of each of the slit grooves is larger than 30%, it is difficult to secure the area required for the inner spherical surface of the outer joint member, which leads to reduction of strength and deterioration of durability.
  • an offset angle of a ball track be set to range from 11.0° to 15.0°, the ball track being formed of each of the plurality of track grooves of the outer joint member and corresponding one of the plurality of track grooves of the inner joint member in cooperation with the plurality of track grooves of the outer joint member.
  • the offset angle represents an angle which a curvature center of each of the plurality of track grooves of the outer joint member and a curvature center of each of the plurality of track grooves of the inner joint member form together with respect to a ball center.
  • a spherical angle formed at a position on a joint-opening side of the outer spherical surface of the inner joint member be set to be equal to or more than 12.5°.
  • the "joint-opening side” represents an opening side of the outer joint member.
  • the "spherical angle” represents an axial angle formed by a joint-opening-side end portion of the outer spherical surface with respect to a curvature center of the outer spherical surface of the inner joint member (joint center).
  • the spherical angle formed at the position on the j oint-opening side of the outer spherical surface of the inner joint member is set to be equal to or more than 12.5°, the following advantage can be obtained: at high operating angles and at the time of high-torque application, even when the large spherical force acts from the outer spherical surface of the inner joint member onto the inner spherical surface of the cage, an area in which the joint-opening-side end portion of the outer spherical surface of the inner joint member comes into contact with the inner spherical surface of the cage can be secured as an area sufficient for bearing the above-mentioned spherical force. By securing of the contact area, the cage is allowed to avoid application of excessive load, and hence smooth rotation can be secured.
  • a step portion be provided in the axial direction between a j oint-opening-side end surface of the inner j oint member and a spline end portion of a shaft hole formed in the inner joint member so that a recessed end surface is formed at a position on an inner side with respect to the joint-opening-side end surface of the inner j oint member.
  • the "joint-opening-side end surface of the inner joint member” represents an end surface at a position on the outer-joint-member opening side in the inner joint member, in other words, on an insertion side of a shaft member to be press-fit to the shaft hole of the inner joint member.
  • the "spline end portion of the shaft hole” represents an end portion at a position on the outer-joint-member opening side of the spline of the shaft hole, in other words, on the insertion side of the shaft member to be press-fit to the shaft hole of the inner joint member.
  • the “step portion in the axial direction” represents a step formed of the joint-opening-side end surface of the inner joint member, the end surface being recessed in the axial direction.
  • the step portion is provided in the axial direction between the joint-opening-side end surface of the inner joint member and the spline end portion of the shaft hole so that the recessed end surface is formed at the position on the inner side with respect to the joint-opening-side end surface.
  • a thickness of the recessed end surface in other words, of a bottom portion of each of the plurality of track grooves (refer to an N portion of a product of the present invention: radial dimension L 2 ) can be increased in comparison with that of the conventional products (refer to an M portion of a conventional product: radial dimension L 1 ).
  • the recessed end surface be formed at a part corresponding to a bottom portion of each of thepluralityof track grooves. Asdescribedabove, when the recessed end surface is formed at the part corresponding to the bottom portion of each of the plurality of track grooves, a ball-contact point does not get out of each of the plurality of track grooves even when the constant velocity universal joint forms a high operating angle. Thus, torque is efficiently and reliably transmitted.
  • a tapered relief portion retracted with respect to the outer spherical surface of the inner joint member be formed at a joint-inner-side end portion of the outer spherical surface, and have a small curvature radius so as to be smoothly continuous with the outer spherical surface.
  • the tapered relief portion retracted with respect to the outer spherical surface of the inner joint member is formed at the joint-inner-side end portion of the outer spherical surface, and has the small curvature radius so as to be smoothly continuous with the outer spherical surface, the radially inner surface of the cage is free from being bitten by the joint-inner-side end portion the inner joint member.
  • a curvature center of each of the plurality of track grooves of the outer joint member be shifted in a radial direction to such a position as to have a radius larger than a radius formed at a position on a joint axis.
  • a curvature center of each of the plurality of track grooves of the inner joint member be shifted in the radial direction to such a position as to have a radius smaller than a radius formed at a position on the joint axis.
  • a driving-wheel bearing unit can be obtained which includes a fixed type constant velocity universal joint having the structure described above and a wheel bearing including the hub wheel coupled to the stem portion extending in the axial direction from the outer joint member of the fixed type constant velocity universal joint.
  • the projection-recess fitting structure is configured in which the projecting portions extending in the axial direction are formed at the plurality of parts in the circumferential direction along any one of the inner diameter of the hub wheel and the outer diameter of the stem portion of the outer joint member, and, by press-fitting of the any one of the inner diameter and the outer diameter to the another of the inner diameter and the outer diameter, the recessed portions to be closely fitted to the projecting portions are formed along the another of the inner diameter and the outer diameter.
  • the projection-recess fitting structure it is effective to form, by transferring of shapes of the projecting portions formed along any one of the inner diameter of the hub wheel and the outer diameter of the stem portion of the outer joint member onto the another of the inner diameter and the outer diameter, which has hardness lower than that of the projecting portions, the recessed portions to be closely fitted to the projecting portions along the another of the inner diameter and the outer diameter, the transferring being caused by elastic deformation at the time of press fitting.
  • the shapes of the projecting portions are transferred onto a recessed-portion forming surface on a counterpart side.
  • the recessed-portion forming surface enters a state of being slightly elastically deformed.
  • the projecting portions are allowed to move in the axial direction.
  • the elastic deformation of the recessed-portion forming surface restores. With this, the entire of recessed-portion fitting parts of the projecting portions is brought into close contact with the recessed portions corresponding thereto, and hence the outer joint member and the hub wheel can be firmly coupled to and integrated with each other.
  • the hub wheel and the outer joint member are coupled to each other so as to be separable by the axial pulling-out force imparted thereto.
  • the hub wheel and the outer joint member are separable from each other, and hence maintenance work on the driving-wheel bearing device is facilitated in which any one of the constant velocity universal joint and the wheel bearing are replaced.
  • the components including the outer joint member, the inner joint member, the plurality of balls, and the cage are combined with each other based on the matching in which the plurality of balls and the cage each having the rank corresponding to the measured value of the PCD of the arbitrarily selected outer joint member and to the measured value of the PCD of the arbitrarily selected inner joint member are selected with respect to the arbitrarily selected outer joint member and the arbitrarily selected inner joint member.
  • the conventional matching is not performed in which all the components of the outer joint members, the inner joint members, the plurality of balls, and the cages are ranked, and then the components including the outer joint members, the inner joint members, the plurality of balls, and the cages are selected and combined with each other.
  • the components can be assembled rapidly and easily, and hence the yield can be increased and workability can be enhanced. Therefore, cost of the constant velocity universal joint can be reduced.
  • a Birfield type constant velocity universal joint (BJ) is illustrated as an example of one of fixed type constant velocity universal joints.
  • a constant velocity universal joint 1 includes, as main components, an outer joint member 10, an inner joint member 20, balls 30, and a cage 40.
  • the constant velocity universal joint 1 includes a structure in which an inner component 50 including the inner joint member 20, the balls 30, and the cage 40 is housed so as to be capable of angular displacement with respect to the outer joint member 10.
  • the outer joint member 10 has a cup-like shape so as to open at one end and an inner spherical surface 14 equiangularly provided with a plurality of track grooves 12 extending in an axial direction.
  • the inner joint member 20 has an outer spherical surface 24 equiangularly provided with a plurality of track grooves 22 extending in the axial direction in pairs with the track grooves 12 of the outer joint member 10.
  • the balls 30 are interposed between the track grooves 12 of the outer joint member 10 and the track grooves 22 of the inner joint member 20 so as to transmit torque.
  • the cage 40 is interposed between the inner spherical surface 14 of the outer joint member 10 and the outer spherical surface 24 of the inner joint member 20 so as to hold the balls 30.
  • the plurality of balls 30 are respectively housed in pockets 42 formed in the cage 40 and equiangularly arranged.
  • the number of balls 30 is arbitrary.
  • Each of the ball tracks formed of the track grooves 12 of the outer joint member 10 and the track grooves 22 of the inner joint member 20 in cooperation with each other exhibits a wedge-like shape of increasing in diameter to an opening side of the outer joint member 10.
  • the outer joint member 10 includes a cup-shaped mouth portion 16 housing the inner component 50 including the inner joint member 20, the balls 30, and the cage 40, and a stem portion 18 extending in the axial direction integrally from a bottom portion of the mouth portion 16.
  • the stem portion 18 has an outer peripheral surface provided with a spline 11 for coupling with respect to a wheel bearing 100 described later (refer to Figs. 22 and 26 ).
  • the inner joint member 20 includes a shaft hole 26 provided with a spline 28 for coupling with respect to a shaft 60 (refer to Figs. 12 and 17 ).
  • the track grooves 12 of the outer joint member 10 and the track grooves 22 of the inner joint member 20 are formed by cold-forging finishing.
  • the components including the outer joint member 10, the inner joint member 20, the balls 30, and the cage 40 are assembled to each other based on simple matching in which the balls 30 and the cage 40 each having a rank corresponding to measured values of PCDs of the outer joint member 10 and the inner joint member 20, each of which has been arbitrarily selected, are selected with respect to the arbitrarily selected outer joint member 10 and the arbitrarily selected inner joint member 20.
  • the track grooves 12 of the outer joint member 10 and the track grooves 22 of the inner joint member 20 are formed by cold-forging finishing, and hence the track grooves 12 and 22 are formed only by cold-forging finishing.
  • many conventional machine processes performed after cold forging can be omitted such as a trimming process and a grinding process.
  • a yield increases, and hence cost of the constant velocity universal joint 1 can be reduced.
  • assembly of the components based on the above-mentioned simple matching is performed by selection of the balls 30 and the cage 40 with respect to the outer joint member 10 and the inner joint member 20 which are respectively provided with the track grooves 12 and 22 formed by cold-forging finishing.
  • the simple matching is performed by the following procedure.
  • cages 40 having pocket widths in conformity with outer diameters of the balls 30 are ranked according to the outer diameters of the balls.
  • the balls 30 and the cages 40 having the pocket widths in conformity with the outer diameters of the balls 30 are ranked into, for example, three ranks: "large”; “medium”; and "small”.
  • PCDs of the arbitrarily selected outer joint member 10 and the arbitrarily selected inner joint member 20 are measured, and based thereon, the balls 30 and the cage 40 each having a rank corresponding to measured values of the PCDs of the arbitrarily selected outer joint member 10 and the arbitrarily selected inner joint member 20 are selected with respect to the arbitrarily selected outer joint member 10 and the arbitrarily selected inner joint member 20.
  • the balls 30 and the cage 40 of the "medium" rank are selected.
  • the balls 30 and the cage 40 of the "large” rank are selected.
  • the balls 30 and the cage 40 of the "small” rank are selected.
  • the components including the outer joint member 10, the inner joint member 20, the balls 30, and the cage 40 are assembled to each other based on the simple matching in which the balls 30 and the cage 40 each having the rank corresponding to the measured values of the PCDs of the arbitrarily selected outer joint member 10 and the arbitrarily selected inner joint member 20 are selected with respect to the arbitrarily selected outer joint member 10 and the arbitrarily selected inner joint member 20.
  • conventional matching (refer to Fig. 28 ) is not performed, in which all the components of outer joint members 210, inner joint members 220, balls 230, and cages 240 are ranked, and then the components including the outer joint members 210, the inner joint members 220, the balls 230, and the cages 240 are selected and combined with each other.
  • the components can be assembled rapidly and easily, and hence a yield can be increased and workability can be enhanced. Therefore, cost of the constant velocity universal joint 1 is easily reduced.
  • PCD gaps of the ball tracks formed of the track grooves 12 of the outer joint member 10 and the track grooves 22 of the inner joint member 20 in cooperation with each other are defined to range from 0 to +0.2 mm.
  • the "PCD (pitch circle diameter) gap” represents a difference between the PCD of the ball 30 in a state of being held in contact with the track groove 12 of the outer joint member 10 (outer-race PCD) and the PCD of the ball 30 in a state of being held in contact with the track groove 22 of the inner joint member 20 (inner-race PCD).
  • the components including the outer joint member 10, the inner joint member 20, the balls 30, and the cage 40 are combined with each other by the requisite-minimum simple matching.
  • abnormal noise generated by backlash of the components can be suppressed to the requisite minimum, with operability of the constant velocity universal joint 1 being secured.
  • the PCD gap is smaller than 0 mm, it is difficult to secure the operability of the constant velocity universal joint 1.
  • the PCD gap is larger than +0.2 mm, the backlash of the components increases, which leads to generation of abnormal noise.
  • a pocket gaps of the pockets 42 of the cage 40 housing the balls 30 are defined to range from -0.05 to 0 mm.
  • the symbol "-" of the numerical value of the pocket gap represents an interference.
  • the "pocket gap” represents a difference between a width in the axial direction of the pocket 42 of the cage 40 (cage-pocket width) and the outer diameter of the ball 30 (ball diameter).
  • the components including the outer joint member 10, the inner joint member 20, the balls 30, and the cage 40 are combined with each other by the requisite-minimum simple matching.
  • abnormal noise generated by backlash of the components can be suppressed to the requisite minimum, with operability of the constant velocity universal joint 1 being secured.
  • the pocket gap in the cage 40 is smaller than -0.050 mm, the interference between the pocket 42 and the ball 30 becomes excessive, which leads to deterioration of durability of the constant velocity universal joint 1.
  • the pocket gap is equal to or more than 0 mm, backlash of the ball 30 occurs in the pocket 42, which leads to generation of abnormal noise.
  • each of the track groove 12 of the outer joint member 10 and the track groove 22 of the inner joint member 20 has a lateral-sectional Gothic arch shape of being held in angular contact with the ball 30.
  • Fig. 4 illustrates the lateral sectional view of each of the track groove 12 of the outer joint member 10 and the track groove 22 of the inner joint member 20.
  • Each of the track grooves 12 and 22 having the Gothic arch shapes respectively include two ball-contact points P and Q (ball-contact angle ⁇ ) of coming in angular contact with the ball 30.
  • the ball-contact angle ⁇ formed at each of the two ball-contact points P and Q of coming in angular contact with the ball 30 range from 35 to 45°.
  • the ball-contact angle ⁇ By setting of the ball-contact angle ⁇ within the range defined as described above, a contact state of the ball 30 with respect to the track grooves 12 and 22 can be stabilized.
  • the ball-contact angle ⁇ is smaller than 35°, track-surface pressure becomes higher, which may lead to a risk of deterioration of durability.
  • the ball-contact angle ⁇ is larger than 45°, margins allowing the ball to climb onto track shoulder portions at high operating angles decrease.
  • the ball climbs onto the track shoulder portions while forming a contact ellipse, which may lead to a risk of chipping of the track shoulder portions, and the like.
  • the cutout round portions 12a and 22a may be formed not by cold-forging finishing but by a machining process such as lathing after cold forging and grinding finishing after heat treatment.
  • the track grooves 12 and the cutout round portions 12a of the outer joint member 10 and the track grooves 22 and the cutout round portions 22a of the inner joint member 20 are formed by simultaneous cold-forging finishing.
  • the track grooves 12 and the cutout round portions 12a of the outer joint member 10 and the track grooves 22 and the cutout round portions 22a of the inner joint member 20 are formed by simultaneous cold-forging finishing, it is unnecessary to perform, after formation of the track grooves 12 and 22, a machining process such as lathing and grinding finishing after heat treatment.
  • the track grooves 12 and 22 and the cutout round portions 12a and 22a are formed only by simultaneous cold-forging finishing, with the result that formation of the cutout round portions can be simplified, and cost of the constant velocity universal joint 1 can be reduced.
  • the cutout round portions 12a and 22a are formed only at the parts corresponding to the ball-contact points at the opening end of the track groove 12 of the outer joint member 10 and the opening end of the track groove 22 of the inner joint member 20, as illustrated in Figs. 5b and 6b , the cutout round portions 12a and 22a may be provided respectively over the opening end of the track groove 12 of the outer joint member 10 and over the opening end of the track groove 22 of the inner joint member 20.
  • the cutout round portions 12a and 22a are provided as described above respectively over the opening end of the track groove 12 of the outer joint member 10 and over the opening end of the track groove 22 of the inner joint member 20, the cutout round portions 12a and 22a constitute track-inlet chamfers described later.
  • inlet chamfers 12b formed along the entire opening periphery of the outer joint member 10
  • track chamfers 12c formed along boundary portions between the inner spherical surface 14 and the track grooves 12
  • track-inlet chamfers 12a formed along boundary portions between the track grooves 12 and the inlet chamfers 12b.
  • a boot made of a resin or rubber is mounted for the purpose of preventing leakage of grease filling an inside of the joint and intrusion of water and foreign matter from an outside of the joint.
  • parts except for a boot-attachment recessed groove 13 formed in an outer peripheral surface of the opening end of the outer joint member 10 are formed by cold-forging finishing.
  • the inlet chamfers 12b, the track chamfers 12c, and the track-inlet chamfers 12a of the outer joint member 10 are formed by cold-forging finishing, and hence the inlet chamfers 12b, the track chamfers 12c, and the track-inlet chamfers 12a are formed only by cold-forging finishing.
  • many conventional machine processes performed after cold forging can be omitted such as a trimming process and a grinding process.
  • a yield further increases, and hence cost of the constant velocity universal joint 1 can be further reduced.
  • the parts except for the boot-attachment recessed groove 13 formed in the outer peripheral surface of the outer joint member 10 are formed by cold-forging finishing, therefore the outer peripheral surface can be endowed with higher hardness, and torsional strength can be increased.
  • work man-hours are reduced, and hence cost of the constant velocity universal joint 1 can be reduced.
  • the following are formed by cold-forging finishing: track chamfers 22c formed along boundary portions between the outer spherical surface 24 and the track grooves 22 of the inner joint member 20; and the track-inlet chamfers 22a formed along boundary portions between both end surfaces of the inner joint member 20 and the track grooves 22.
  • the track chamfers 22c and the track-inlet chamfers 22a of the inner joint member 20 are formed by cold-forging finishing, and hence the track chamfers 22c and the track-inlet chamfers 22a are formed only by cold-forging finishing.
  • many conventional machine processes performed after cold forging can be omitted such as a trimming process and a grinding process.
  • a yield further increases, and hence cost of the constant velocity universal joint 1 can be further reduced.
  • the track-inlet chamfers 12a of the outer joint member 10 are formed by cold-forging finishing, it suffices that the track grooves 12 and the track-inlet chamfers 12a of the outer joint member 10 are formed by simultaneous cold-forging finishing.
  • the track grooves 12 and the track-inlet chamfers 12a of the outer joint member 10 are formed by simultaneous cold-forging finishing, it is unnecessary to perform, after formation of the track grooves 12, a machining process such as lathing and grinding finishing after heat treatment.
  • the track grooves 12 and the track-inlet chamfers 12a are formed only by simultaneous cold-forging finishing, with the result that formation of the track-inlet chamfers can be simplified, and cost of the constant velocity universal joint 1 can be reduced.
  • the track chamfers 12c formed along theboundaryportions between the inner spherical surface 14 and the track grooves 12 of the outer joint member 10 and track chamfers 22c formed along boundary portions between the outer spherical surface 24 and the track grooves 22 of the inner joint member 20 each exhibit a round shape as illustrated in Fig. 2 in an enlarged manner.
  • the round shapes of each of the track chamfers 12c and 22c are formed successively to provide smooth continuation respectively between the track grooves 12 and the inner spherical surface 14 and between the track grooves 22 and the outer spherical surface 24.
  • the track chamfers 12c formed along the boundary portions between the inner spherical surface 14 and the track grooves 12 of the outer joint member 10 and the track chamfers 22c formed along the boundary portions between the outer spherical surface 24 and the track grooves 22 of the inner joint member 20 are each formed in the round shape, stress concentration thereat can be avoided.
  • the track chamfers 12c and 22c may be formed not by cold-forging finishing but by a machining process such as lathing after cold forging and grinding finishing after heat treatment.
  • the track grooves 12 and the track chamfers 12c of the outer joint member 10 and the track grooves 22 and the track chamfers 22c of the inner joint member 20 are formed by simultaneous cold-forging finishing.
  • the track grooves 12 and the track chamfers 12c of the outer joint member 10 and the track grooves 22 and the track chamfers 22c of the inner joint member 20 are formed by simultaneous cold-forging finishing, it is unnecessary to perform, after formation of the track grooves 12 and 22, a machining process such as lathing and grinding finishing after heat treatment.
  • the track grooves 12 and 22 and the track chamfers 12c and 22c are formed only by simultaneous cold-forging finishing, with the result that formation of the track chamfers can be simplified, and cost of the constant velocity universal joint 1 can be reduced.
  • slit grooves 12d are formed in the axial direction between the track grooves 12 adjacent to each other in a circumferential direction along the inner spherical surface 14 of the outer joint member 10.
  • the slit grooves 12d are formed to reach the inner spherical surface 14 from an opening-end surface of the outer joint member 10 via the inlet chamfers 12b.
  • the number of the slit grooves 12d is arbitrary.
  • a width dimension of each of the slit grooves 12d is set to range from 5% to 30% of a maximum width dimension of the inner spherical surface 14 between the track grooves 12 adjacent to each other in the circumferential direction.
  • the inner spherical surface 14 can be formed with desired shape accuracy.
  • the width dimension of each of the slit grooves 12d is set to range from 5% to 30%, it is easy to demold the outer joint member 10 from the molding die at the time of cold forging.
  • an area required for the inner spherical surface 14 of the outer joint member 10 can be secured, and hence required strength and durability can be secured.
  • the width dimension of each of the slit grooves 12d is smaller than 5%, it is difficult to demold the outer joint member 10 from the molding die at the time of cold forging.
  • the width dimension of each of the slit grooves 12d is larger than 30%, it is difficult to secure the area required for the inner spherical surface 14 of the outer joint member 10, which leads to reduction of strength and deterioration of durability.
  • a curvature center O 1 of the track groove 12 of the outer joint member 10 and a curvature center O 2 of the track groove 22 of the inner joint member 20 are offset to each other in the axial direction with respect to a joint center O by equal distances F onto opposite sides (the curvature center O 1 of the track groove 12 is offset on an opening side of the joint, and the curvature center O 2 of the track groove 22 is offset on an inner-portion side of the joint).
  • the ball track exhibits the wedge-like shape of being wide on the opening side and gradually narrowed to the inner-portion side.
  • both a curvature center of an outer spherical surface 44 of the cage 40 and a curvature center of the inner spherical surface 14 of the outer joint member 10 correspond to the joint center O, the inner spherical surface 14 being held in sliding contact with the outer spherical surface 44.
  • both a curvature center of an inner spherical surface 46 of the cage 40 and a curvature center of the outer spherical surface 24 of the inner joint member 20 also correspond to the joint center O, the outer spherical surface 24 being held in sliding contact with the inner spherical surface 46.
  • an offset angle ⁇ is set to range from 11.0° to 15.0°.
  • the offset angle ⁇ is lower than offset angles of conventional products (approximately 16.0°).
  • the track grooves 12 and 22 are deeper at shallow parts than those of the conventional products.
  • the balls 30 are less liable to climb onto the shoulder portions of the track grooves 12 and 22 while forming contact ellipses, and hence chipping of the shoulder portions and the like are prevented.
  • the track grooves 12 and 22 can be endowed with higher strength and durability.
  • a thickness of the cage 40 can be increased, and hence the cage 40 can be endowed with higher strength and prolonged life. Still further, as described above, when the offset angle ⁇ falls within the above-mentioned range, operability can be satisfactorily maintained.
  • the respective track grooves 12 and 22 of the outer joint member 10 and the inner joint member 20 can be endowed with higher strength and durability.
  • the track grooves 12 of the outer joint member 10 and the track grooves 22 of the inner joint member 20 are easily formed by cold-forging finishing.
  • a jumping-out force of the ball 30 with respect to the joint-opening side is weakened in comparison with that of the conventional products, and hence generation of slapping noise owing to the axial force of the ball 30 can be suppressed.
  • the applicants of the present invention confirmed whether or not the range of the offset angler ⁇ defined as described above was optimum.
  • the crosswise operability was evaluated based on presence or absence of clicking at the time when the shaft was bent up to a maximum operating angle in a plane including opposed ball tracks and then the shaft was similarly bent in a plane perpendicular to the plane described above. Further, the durability was evaluated under the following conditions: load torque: 834 N ⁇ m (85 kgf ⁇ m); number of rotations: 230 rpm; and operating angle: 6°.
  • Fig. 10 shows results of the tests. Note that, the symbols and meanings thereof in Fig. 10 are as follows: ⁇ : problematic; ⁇ : poor; ⁇ : normal; and ⁇ : good (the same applies to description hereinbelow).
  • the inner joint member 20 in the constant velocity universal joint 1 forms, as illustrated in Fig. 11 , a spherical angle ⁇ equal to or more than 12.5° at a position on a joint-opening side of the outer spherical surface 24.
  • the spherical angle ⁇ is an axial angle formed by a joint-opening-side end portion of the outer spherical surface 24 with respect to the curvature center of the outer spherical surface 24 of the inner joint member 20 (joint center O).
  • the spherical angle ⁇ is set to be equal to or more than 12.5° for the following reason.
  • Figs. 12 and 13 each illustrate a state in which the shaft 60 (broken lines in Fig. 12 ) as a drive shaft spline-fitted to the inner joint member 20 forms a maximum operating angle ⁇ .
  • a maximum operating angle ⁇ When torque is applied to the shaft 60, spherical forces are generated between the inner joint member 20 and the cage 40 and between the cage 40 and the outer joint member 10.
  • the spherical force which acts between the inner joint member 20 and the cage 40 at the maximum operating angle under a state in which the shaft 60 forms the maximum operating angle ⁇ at a phase angle between 0° and 360° (refer to Fig.
  • a large spherical force is generated particularly at a phase angle between 240° and 340°.
  • the spherical force which has been zero, is rapidly generated approximately at a phase angle of 240°.
  • Fig. 14 illustrates the contact state of the inner joint member 20 and the cage 40.
  • Fig. 14 is a sectional view taken along the line C-O-C of Fig. 13 , in which a side of the phase angle of 240° of Fig. 13 is on an upper side and a side of the phase angle of 60° of Fig. 13 is on a lower side.
  • the spherical angle ⁇ equal to or more than 12.5° is formed at the position on the joint-opening side of the outer spherical surface 24 of the inner joint member 20 (refer to Fig. 11 ).
  • the joint-opening-side end portion of the outer spherical surface 24 of the inner joint member 20 reliably comes into contact with an inlet side of the inner spherical surface 46 of the cage 40.
  • a contact area can be sufficiently secured so that the above-mentioned spherical force can be born.
  • Fig. 15 illustrates the inner joint member 20 as a component constituting the constant velocity universal joint 1, in which a lower half with respect to a center line illustrates the inner joint member 20 of a product of the present invention and an upper half with respect to the center line illustrates the inner joint member 220 as a conventional product for comparison with the product of the present invention.
  • a step portion 25 is provided in the axial direction between a joint-opening-side end surface 23 of the inner joint member 20 and a spline end portion 28a of the shaft hole 26 so that a recessed end surface 27 is formed at a position on the inner side with respect to the joint-opening-side end surface 23.
  • the joint-opening-side end surface 23 of the inner joint member 20 and the spline end portion 28a of the shaft hole 26 are positioned on an insertion side of the shaft 60 to be press-fit to the shaft hole 26 of the inner joint member 20, that is, the opening side of the outer joint member 10.
  • a thickness of the inner joint member 20 is reduced for weight reduction and compactification of the constant velocity universal joint 1, as illustrated in Fig. 15 , as for the conventional product, a thickness is reduced in a bottom portion of a track groove 222 in a joint-opening-side end surface 223 of the inner joint member 220 (radial dimension L 1 of a M portion).
  • the step portion 25 is provided in the axial direction between the joint-opening-side end surface 23 of the inner joint member 20 and the spline end portion 28a of the shaft hole 26 so that the recessed end surface 27 is formed at the position on the inner side with respect to the joint-opening-side end surface 23.
  • a thickness of a bottom portion of the track groove 22 in the recessed end surface 27 (radial dimension L 2 of an N portion) can be increased in comparison with that of the conventional product (radial dimension L 1 of theMportion) (L 2 >L 1 ).
  • the thickness of the recessed end surface 27 of the inner joint member 20 is increased in comparison with that of the conventional product.
  • strength of the inner joint member 20 can be sufficiently secured.
  • the constant velocity universal joint 1 is weight-reduced and compactified, and the inner joint member 20 is endowed with higher strength.
  • the radial dimension L 2 of the recessed end surface 27 positioned on the inner side with respect to the joint-opening-side end surface 23 of the inner joint member 20 is set to be equal to or more than 1 mm.
  • the radial dimension L 2 of the recessed end surface 27 is smaller than 1 mm, stress concentration is liable to occur in the recessed end surface 27 at high operating angles and at the time of high-torque application. As a result, it is difficult to sufficiently secure strength of the inner joint member 20.
  • the recessed end surface 27 positioned on the inner side with respect to the joint-opening-side end surface 23 of the inner joint member 20 is formed at a part corresponding to the bottom portion of the track groove 22.
  • a ball-contact point P in other words, the contact ellipse formed at the time when the ball 30 is held in contact with the track groove 22 of the inner joint member 20 does not get out of the track groove 22.
  • the ball 30 described above represents a ball 30 positioned at an innermost portion of the track groove 12 of the outer joint member 10 (inlet-nearest portion of the track groove 22 of the inner joint member 20).
  • FIG. 18 illustrates a comparison example with respect to Fig. 17 .
  • the parts same as those in Fig. 17 are denoted by the same reference symbols with dashes, and redundant description thereof is omitted.
  • a radially outer part with respect to a recessed end surface formed at a part corresponding to a bottom portion of a track groove 22' (dotted-line part a in the figure) is cut off, in other words, when an axial width of an inner joint member 20' is merely reduced, a thickness of a joint-opening-side end surface 23' of the inner joint member 20' can be secured.
  • a swellingpart (dotted-linepart in the figure) is cut off, which swells from a bottom portion in the track groove 22' while being positioned on the radially outer part with respect to the recessed end surface described above.
  • a ball-contact point P' gets out of the track groove 22' of the inner joint member 20'.
  • a tapered relief portion 24a retracted with respect to the outer spherical surface 24 having a curvature radius R.
  • the tapered relief portion 24a has a curvature radius R 1 set to be smaller than the curvature radius R of the outer spherical surface 24 so as to be smoothly continuous with the outer spherical surface 24.
  • the tapered relief portion 24a is retracted to a radially inner side with respect to an inner-side end portion of a case where the relief portion 24a is not provided (range illustrated by an imaginary line of Fig. 19 ).
  • a range H of the relief portion 24a (range from a joint-inner-side end surface 29 of the inner joint member 20 to an intersection of the tapered relief portion 24a and the outer spherical surface 24) to be equal to or smaller than 3 mm.
  • the inner spherical surface 46 of the cage 40 is free from being bitten by the joint-inner-side end portion of the inner joint member 20, which enables smooth rotation. As a result, excessive load onto the cage 40 can be reduced, and the cage 40 can be endowed with higher strength.
  • the contact area of the inner joint member 20 and the cage 40 can be effectively secured. As a result, surface pressure between the inner joint member 20 and the cage 40 and heat generation can be suppressed, which leads to prolongation of a life.
  • the relief portion 24a is excessively large, the contact area of the inner joint member 20 and the cage 40 is reduced. As a result, the surface pressure between the inner joint member 20 and the cage 40 becomes higher and heat generation is promoted, which may lead to a risk of shortening of the life of the constant velocity universal joint 1.
  • a curvature center O 1 ' of the track groove 12 of the outer joint member 10 in the constant velocity universal joint 1 is shifted as illustrated in Fig. 20 in the radial direction to such a position as to have a radius larger than a radius formed at the position on a joint axis.
  • a curvature center O 2 ' of the track groove 22 of the inner joint member 20 is shifted as illustrated in Fig. 21 in the radial direction to such a position as to have a radius smaller than the radius formed at the position on the joint axis.
  • the constant velocity universal joint 1 described above in this embodiment constitutes a driving-wheel bearing unit when the stem portion 18 to the wheel bearing 100 are coupled to each other so that torque can be transmitted, the stemportion 18 extending in the axial direction integrally from the mouth portion 16 in which the inner component 50 including the inner joint member 20, the balls 30, and the cage 40 is housed.
  • Fig. 22 illustrates, as an example, a structure of a driving-wheel bearing unit in which the constant velocity universal joint 1 of Fig. 1 is coupled to the wheel bearing 100.
  • the driving-wheel bearing unit includes, as main components, a hub wheel 110 and an inner race 12 0 as inner members, double row rolling elements 130 and 140, an outer race 150 as an outer member, and the constant velocity universal joint 1.
  • the hub wheel 110, the inner race 120, the rolling elements 130 and 140, and the outer race 150 which are described above constitute the wheel bearing 100.
  • a side on a vehicle outer side is referred to as an outboard side (left side of the figure), and a side on a center is referred to as an inboard side (right side of the figure).
  • the hub wheel 110 has an outer peripheral surface provided with an outboard-side inner raceway surface 112, and includes a wheel-attachment flange 114 to which a wheel (not shown) is attached. Hub bolts 116 for fixing a wheel disc are embedded equiangularly to the wheel-attachment flange 114.
  • the inner race 120 is fitted to a small-diameter step portion 118 formed in an inboard-side outer peripheral surface of the hub wheel 110, and an inboard-side inner raceway surface 122 is formed in an outer peripheral surface of the inner race 120.
  • the hub wheel 110 is manufactured by lathing or forging.
  • the inner race 120 is press-fitted with a proper interference for the purpose of preventing creep.
  • Double row inner raceway surfaces are constituted by the outboard-side inner raceway surface 112 formed in the outer peripheral surface of the hub wheel 110 and the inboard-side inner raceway surface 122 formed in the outer peripheral surface of the inner race 120.
  • the inner race 120 is press-fitted to the small-diameter step portion 118 of the hub wheel 110, and then an end portion of the small-diameter step portion 118 of the hub wheel 110 is plastically deformed outward in the radial direction by orbital forming. With this, a caulked portion 113 is formed.
  • the caulked portion 113 retains the inner race 120 and is integrated with the hub wheel 110 so as to impart preload to the wheel bearing 100.
  • the outer race 150 has an inner peripheral surface provided with double row outer raceway surfaces 152 and 154 respectively facing the inner raceway surface 112 of the hub wheel 110 and the inner raceway surface 122 of the inner race 120.
  • the outer race 150 is fitted to a knuckle (not shown) extending from a suspension of the vehicle, and is retained by a snap ring 151.
  • the wheel bearing 100 has a double row angular ball bearing structure, in which the rolling elements 130 and 140 are respectively interposed between the inner raceway surfaces 112 and 122 and the outer raceway surfaces 152 and 154 so that the rolling elements 130 and 140 in the respective double rows are respectively and equiangularly supported by retainers 132 and 142, the inner raceway surfaces 112 and 122 being respectively formed in the outer peripheral surfaces of the hub wheel 110 and the inner race 120, the outer raceway surfaces 152 and 154 being formed in the inner peripheral surface of the outer race 150.
  • predetermined bearing gaps are set in the wheel bearing 100.
  • a pair of seals 134 and 144 for respectively sealing an annular space between the outer race 150 and the hub wheel 110 and an annular space between the outer race 150 and the inner race 120 are fitted along inner diameters of both end portions of the outer race 150 in a manner of being held in sliding contact with the outer peripheral surfaces of the hub wheel 110 and the inner race 120.
  • a shaft hole 115 of the hub wheel 110 illustrated in Fig. 22 is formed in a simple cylindrical shape (refer to Fig. 23 ) freefromafemalesplineprovided with recessed portions which are formed, at a plurality of parts in a circumferential direction, in an inner peripheral surface thereof and which extend in the axial direction.
  • the driving-wheel bearing unit includes the spline 11 (refer to Fig. 24 ) provided with projecting portions 11a which are formed, at a plurality of parts in the circumferential direction, on the outer peripheral surface of the stem portion 18 of the outer joint member 10 of the constant velocity universal joint 1 and which extend in the axial direction.
  • the driving-wheel bearing unit has a projection-recess fitting structure S in which, by press-fitting of the stem portion 18 of the outer joint member 10 to the shaft hole 115 of the hub wheel 110, recessed portions 115a to be closely fitted to the spline 11 are formed in the shaft hole 115 of the hub wheel 110 as illustrated in Fig. 25 .
  • the driving-wheel bearing unit has a structure in which the hub wheel 110 and the outer joint member 10 are firmly coupled to each other.
  • the inner peripheral surface of the shaft hole 115 of the hub wheel 110 has not undergone curing treatment, in other words, remains a raw material.
  • the spline 11 of the stem portion 18 of the outer joint member 10 has undergone curing treatment by induction hardening.
  • induction hardening in which a hardening range and a hardening depth can be easily controlled, is suitable as curing treatment on the spline 11 of the stem portion 18 of the outer joint member 10
  • other curing treatment may be employed.
  • the hub wheel 110 is basically a raw material which has not undergone heat treatment, heat treatment may be performed as long as surface hardness of the spline 11 of the stem portion 18 is not exceeded.
  • the shaft hole 115 of the hub wheel 110 is free from a spline, and the outer peripheral surface of the stem portion 18 is provided with the spline 11.
  • the shaft hole 115 of the hub wheel 110 may be provided with a spline, and the outer peripheral surface of the stem portion 18 may be free from the spline so that the stem portion 18 is formed in a simple columnar shape.
  • functions and advantages can be obtained, which are the same as those in the case where the shaft hole 115 of the hub wheel 110 is free from a spline and the outer peripheral surface of the stem portion 18 is provided with the spline 11.
  • the hub wheel 110 and the outer joint member 10 can be firmly coupled to each other by the proj ection-recess fitting structure S.
  • the caulked portion 113 of the hub wheel 110 and a shoulder portion 17 of the outer joint member 10 are held in contact with each other. In this case, positioning is performed on the stem portion 18 of the outer joint member 10.
  • dimensional accuracy of the bearing device and an axial length of the projection-recess fitting structure S can be stabilized, with the result that a torque-transmission property can be enhanced.
  • the driving-wheel bearing unit is illustrated in which the constant velocity universal joint 1 and the wheel bearing 100 are integrated with each other.
  • a driving-wheel bearing unit may be employed in which the constant velocity universal joint 1 and the wheel bearing 100 are separably coupled to each other. Note that, in Fig. 26 , the parts same as those in Fig. 22 are denoted by the same reference symbols, and redundant description thereof is omitted.
  • the hub wheel 110 and the outer joint member 10 are coupled to each other so as to be separable by an axial pulling-out force imparted thereto.
  • the shape of the spline 11 is transferred to the shaft hole 115 of the hub wheel 110 along with plastic deformation and trimming, the shaft hole 115 being the recessed-portion forming surface on the counterpart side.
  • the hub wheel 110 enters the state of being slightly increased in inner diameter by elastic deformation.
  • the spline 11 is allowed to move in the axial direction.
  • the inner diameter of the hub wheel 110 should restore the original diameter by an elastic restoring force, and hence is reduced.
  • the caulked portion 113 imparts preload to the wheel bearing 100.
  • the stem portion 18 of the outer joint member 10 can be press-fitted without consideration of a preload amount, and a coupling property (assembly property) of the hub wheel 110 and the outer joint member 10 can be enhanced. Note that, it suffices that the fastening force of the bolt 80 is exerted to such an extent that the hub wheel 110 and the outer joint member 10 are fixed to each other.
  • a gap n is formed between the caulked portion 113 as a joint-side end portion of the hub wheel 110 and the shoulder portion 17 as a hub-wheel-facing end portion of the outer joint member 10.
  • the caulked portion 113 of the hub wheel 110 and the shoulder portion 17 of the outer joint member 10 enter the non-contact state with respect to each other, and hence abnormal noise is prevented from being generated owing to contact of the caulked portion 113 of the hub wheel 110 and the shoulder portion 17 of the outer joint member 10.
  • the outer joint member 10 and the hub wheel 110 are coupled to each other so as to be separable by the axial pulling-out force imparted thereto.
  • the hub wheel 110 and the outer joint member 10 are separable from each other, and hence maintenance work on the driving-wheel bearing unit is facilitated.
  • any one of the wheel bearing 100 and the constant velocity universal joint 1 is replaced, the wheel bearing 100 including the hub wheel 110, the inner race 120, the outer race 150, and the rolling elements 130 and 140.
  • the bolt 80 is detached as illustrated in Fig.
  • a case is illustrated as an example where the present invention is applied to a driving-wheel bearing device of a type that one of the double row inner raceway surfaces 112 and 122 formed on the inner member including the hub wheel 110 and the inner race 120, in other words, the outboard-side inner raceway surface 112 is formed on the outer periphery of the hub wheel 110 (referred to as third generation) .
  • the present invention is not limited thereto, and is applicable also to a driving-wheel bearing device of a type that the inboard-side inner raceway surface 122 is formed on the shoulder portion 17 of the outer joint member 10 of the constant velocity universal joint 1 (referred to as fourth generation), and also to a driving-wheel bearing device of a type that a pair of inner races are press-fitted to the outer periphery of the hub wheel 110, and the outboard-side inner raceway surface 112 is formed on an outer periphery of one of the inner races and the inboard-side inner raceway surface 122 is formed on an outer periphery of the other of the inner races (referred to as first or second generation).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Forging (AREA)
  • Rolling Contact Bearings (AREA)
EP09824685.3A 2008-11-06 2009-10-06 Verfahren zur herstellung eines universellen gleichlauffestgelenks Not-in-force EP2345823B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008285562A JP5318535B2 (ja) 2008-11-06 2008-11-06 固定式等速自在継手及びその製造方法並びにこの固定式等速自在継手を用いた駆動車輪用軸受ユニット
PCT/JP2009/067380 WO2010052985A1 (ja) 2008-11-06 2009-10-06 固定式等速自在継手及びその製造方法並びにこの固定式等速自在継手を用いた駆動車輪用軸受ユニット

Publications (3)

Publication Number Publication Date
EP2345823A1 true EP2345823A1 (de) 2011-07-20
EP2345823A4 EP2345823A4 (de) 2012-05-02
EP2345823B1 EP2345823B1 (de) 2015-09-09

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EP09824685.3A Not-in-force EP2345823B1 (de) 2008-11-06 2009-10-06 Verfahren zur herstellung eines universellen gleichlauffestgelenks

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US (1) US8499457B2 (de)
EP (1) EP2345823B1 (de)
JP (1) JP5318535B2 (de)
CN (1) CN102209857B (de)
WO (1) WO2010052985A1 (de)

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JP2010112469A (ja) 2010-05-20
US8499457B2 (en) 2013-08-06
CN102209857A (zh) 2011-10-05
WO2010052985A1 (ja) 2010-05-14
CN102209857B (zh) 2014-07-16
US20110212788A1 (en) 2011-09-01
JP5318535B2 (ja) 2013-10-16
EP2345823A4 (de) 2012-05-02
EP2345823B1 (de) 2015-09-09

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